This application claims benefit to German Patent Application Number 10 2019 108 669.8, filed Apr. 3, 2019, which is incorporated in its entirety by reference herein.
The disclosure relates to a compressor, especially a diaphragm pump, and to a method for manufacturing such a compressor.
A diaphragm pump is known, for example, from EP 2 112 377 A2. The known pump includes a motor and a drive unit with at least one swash plate, which periodically compresses a diaphragm body. In such a pump, the motor is typically balanced, so that the motor lacking the drive unit has no imbalance.
It is furthermore known that the drive unit can be balanced, for example, with an eccentric in such a way that the drive unit, when considered separately, has no imbalance. However, when such a pump is operated, vibrations are generated when the diaphragm body is compressed.
It is furthermore known from EP 2 654 511 that pump vibrations occurring outside of a housing, especially when used in vehicle seats, disturb the user acoustically or due to the movement as such, are reduced by springs arranged between motor unit and housing. Such an incorporation of springs in pumps, however, increases the weight, enlarges the housing (i.e. the space needed when incorporating them in a vehicle seat, for example) and increases the cost of such a pump.
A purpose of the disclosure is to eliminate the disadvantage according to the state of the art. In particular, a compressor and a method for producing such a statically and dynamically balanced compressor should be indicated.
The compressor according to the disclosure includes a housing with a first area and a second area, wherein a compressor motor is incorporated into the first area and a diaphragm pump unit of the compressor is incorporated into the second area, wherein the diaphragm pump unit includes at least one diaphragm body and one drive unit, wherein an armature of the motor is operatively connected to the drive unit via a drive axle, wherein the drive unit has a first imbalance and the motor a second imbalance, wherein the size of the second imbalance is designed in such a way that the sum of the first imbalance and of the second imbalance in the system consisting of motor and drive unit coupled with the drive axle results statically and dynamically in zero or at least almost zero. The second imbalance can be especially generated by second weights locally added (e.g. affixed) to the armature of the motor or locally inserted depressions, thereby changing the distribution of masses with regard to the balanced motor. Likewise, the first imbalance can take place by locally adding first weights or a local weight reduction. In case of the drive axle, it can be especially a motor shaft. The drive unit expediently includes a swash plate, a swash plate axle, and an eccentric. The eccentric is expediently connected to the drive axle and the swash plate axle. The eccentric has expediently at least one weight.
The housing can be executed as one single piece. Alternately, the housing includes a first partial housing (which can be the motor housing itself) as first area and a second partial housing for the diaphragm pump unit. The first and second partial housing are then connected to one another.
The compressor according to the disclosure is also dynamically balanced so no disturbing vibrations are generated and thus suspensions do not have to be installed or they can be at least executed in a considerably easier way. The compressor according to the disclosure is particularly suitable for incorporation in vehicle seats for seating comfort functions, e.g. lumbar supports.
In the embodiment, the imbalance of the motor is generated at least by a milled groove on the motor armature. Such a milled groove is especially arranged in a largely cylindrical armature of the motor. The milled groove can extend perpendicularly or parallel to the drive axle. For easier naming, the extension direction of the drive axle will hereinafter be named z-axis. An x-axis and a y-axis form an orthogonal coordinate system to the z-axis.
Expediently, the compressor has on the armature of the motor at least two milled grooves, arranged on opposite sides with regard to an x-axis and/or a y-axis and/or a z-axis. Thus, for example, a first milled groove is arranged on a side of the cylindrical armature that faces the drive unit and a second milled groove on a side of the cylindrical armature that faces away from the drive unit, wherein the first milled groove and the second milled groove cut a plane that includes the drive axle.
The drive unit includes a swash plate, a swash plate axle and an eccentric, wherein the eccentric is connected to the drive axle and the swash plate axle, wherein the eccentric has at least one weight. The drive axle and the swash plate axle have especially an angle α to one another.
In particular, the eccentric has two weights opposite one another, parallel to the drive axle and expediently spaced apart.
The weight or weights can be spherical and/or incorporated into the eccentric. In the embodiment, the weights can be designed to be screwed in the eccentric. Alternately, the weights can also be executed as one single piece with the eccentric.
The method according to the disclosure for manufacturing a compressor according to the disclosure includes the following steps:
Provision of a balanced motor,
Provision of a balanced drive unit and connection to the motor,
Determination of the dynamic imbalance of a system consisting of motor and diaphragm pump unit, which contains the drive unit, and
Generation of a first and second imbalance U1 and U2 that dynamically and statically balance themselves out.
The drive unit expediently includes one swash plate, one swash plate axle, and one eccentric. The eccentric is expediently connected to the drive axle and the swash plate axle that expediently has at least one weight.
The generation of the second imbalance U2 can especially take place by means of a balancing machine, in which an imbalance U2 is entered as target value. The imbalance U2 depends on the position and size of milled grooves or additional weights.
The determination of the dynamic imbalance can take place in tests performed with structurally identical systems consisting of motor and diaphragm pump unit. Alternately, the dynamic imbalance can be determined with a simulation.
In this context, the generation of a second imbalance—especially the insertion of at least one milled groove in the armature—is what compensates for the dynamic imbalance. To create the milled groove, a balancing machine in which the second imbalance U2 is entered as target value, can be especially used.
In another embodiment, the method includes the determination of a residual imbalance in compressors manufactured according to the method and the consideration of the residual imbalance for setting the target value.
The disclosure will now be explained in more detail with reference to the enclosed drawings, which show:
2 Compressor
4 Housing
6 First area
8 Second area
10 Motor
12 Diaphragm pump unit
14 Drive unit
16 Swash plate
18 Drive axle
20 Swash plate axle
22 Diaphragm body
24 Eccentric
26 Weight
28 Milled groove
30 Armature
32 Magnet
34 Brush
A Distance
U1 First imbalance
U2 Second imbalance
α Angle
Number | Date | Country | Kind |
---|---|---|---|
10 2019 108 669.8 | Apr 2019 | DE | national |
Number | Name | Date | Kind |
---|---|---|---|
4507058 | Schoenmeyr | Mar 1985 | A |
4610605 | Hartley | Sep 1986 | A |
4801249 | Kakizawa | Jan 1989 | A |
5230616 | Serizawa | Jul 1993 | A |
5711652 | Van De Venne | Jan 1998 | A |
5738503 | Schmidt-Marloh | Apr 1998 | A |
6382928 | Chang | May 2002 | B1 |
6716005 | Yamakawa | Apr 2004 | B2 |
6843643 | Fukami | Jan 2005 | B2 |
7377756 | Hori | May 2008 | B2 |
7426858 | Otten | Sep 2008 | B2 |
7520734 | Luedtke | Apr 2009 | B2 |
7819636 | Huang | Oct 2010 | B2 |
8596992 | DeDecker | Dec 2013 | B2 |
9217425 | Looi | Dec 2015 | B2 |
9702377 | Wykman | Jul 2017 | B2 |
9784264 | Krebs | Oct 2017 | B2 |
20050025651 | Sowa | Feb 2005 | A1 |
20080292484 | Suh et al. | Nov 2008 | A1 |
20100101407 | Lynn | Apr 2010 | A1 |
Number | Date | Country |
---|---|---|
1914784 | Feb 2007 | CN |
203685529 | Jul 2014 | CN |
203685529 | Jul 2014 | CN |
205089621 | Mar 2016 | CN |
206816477 | Dec 2017 | CN |
10247293 | May 2003 | DE |
102 59 179 | Jul 2004 | DE |
195 01 959 | Jul 2004 | DE |
10 2013 207 741 | Oct 2014 | DE |
0936355 | Aug 1999 | EP |
2112377 | Oct 2009 | EP |
20180103270 | Sep 2018 | KR |
Entry |
---|
German Office Action for application No. DE 102019108669.8, dated Feb. 24, 2022, with English translation. |
German Office Action for Application No. 10 2019 108 669.8, dated Dec. 13, 2019, with English Translation. |
Chinese Office Action dated Nov. 9, 2021. |
Chinese Office Action dated Aug. 1, 2022, for application No. 202010244193.0, with English translation. |
Number | Date | Country | |
---|---|---|---|
20200318634 A1 | Oct 2020 | US |